EP2649331B1 - Radialwälzlager mit losen abstandskörpern zwischen den wälzkörpern und verfahren zum zusammenbau des wälzlagers - Google Patents

Radialwälzlager mit losen abstandskörpern zwischen den wälzkörpern und verfahren zum zusammenbau des wälzlagers Download PDF

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Publication number
EP2649331B1
EP2649331B1 EP11802879.4A EP11802879A EP2649331B1 EP 2649331 B1 EP2649331 B1 EP 2649331B1 EP 11802879 A EP11802879 A EP 11802879A EP 2649331 B1 EP2649331 B1 EP 2649331B1
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EP
European Patent Office
Prior art keywords
bearing
rolling
spacer
radial direction
elements
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Active
Application number
EP11802879.4A
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German (de)
English (en)
French (fr)
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EP2649331A1 (de
Inventor
Sabine Hofmann
Baozhu Liang
Michael Reugels
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SKF AB
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SKF AB
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/37—Loose spacing bodies
    • F16C33/3706—Loose spacing bodies with concave surfaces conforming to the shape of the rolling elements, e.g. the spacing bodies are in sliding contact with the rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/20—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows with loose spacing bodies, e.g. balls, between the bearing balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F16C43/06—Placing rolling bodies in cages or bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

Definitions

  • the present invention is concerned with rolling bearings and in particular with a new cage concept or with a concept that makes it possible to keep the plurality of rolling elements in a rolling bearing relative to each other in a defined minimum distance.
  • rolling bearing cages are used.
  • the size of the rolling elements can be increased itself, so that an overall larger bearing is formed.
  • Snap cages are easy to handle when assembling a bearing because they hold the rolling elements, such as the balls of a ball bearing, by their inherent elasticity, thereby preventing a disassembly of the bearing after assembly.
  • the cage diameter be less than the diameter of the shelf to prevent the bearing or the rolling elements from falling apart.
  • a separate spacer is used between two directly adjacent rolling elements in a rolling bearing, which is geometrically dimensioned so that it ensures a predetermined minimum distance between the two rolling elements.
  • the spacer is made in two parts, that is, it consists of a first, radially inner sub-element and a second, radially outer sub-element.
  • Radially inward in this context means that the sub-element is located completely inside (i.e., closer to the bearing axis) of the radially outer sub-element in the radial direction. That In other words, the radially outer sub-element completely covers the inner sub-element in the radial direction to the outside.
  • an axial direction denotes a direction parallel to the axis of rotation of the bearing and a radial direction any direction perpendicular thereto.
  • the two sub-elements are connected together along a separation surface and together form the spacer element.
  • This compound can be positive, cohesive or cohesive and the interface can have any geometric shape.
  • the interface may have the shape of a T-slot or meander extend, for example, when bonding the contact surface and thus increase the stability of the connection.
  • the separation surface is configured, for example, such that the first sub-element and the second sub-element are connected to each other via a snap mechanism.
  • a spacer which consists of two sub-elements, makes it possible to increase the number of rolling elements, for example, further, if the consisting of at least two sub-elements spacer is mounted last. In this case, the available space on the bearing pitch or the space that is still free between the last rolling elements, can be minimal, since a tilted insertion or mounting of the last spacer is not required due to its bipartite.
  • the inner sub-element or the outer sub-element is introduced and positioned so that it extends into a recess in the inner or outer ring before the second sub-element is also introduced in the axial direction between the two bearing rings , In the final aligned position then the two sub-elements can be connected to the spacer element.
  • the space required for the assembly of the last spacer is minimized and achieved by increasing the number of rolling elements to increase the carrying capacity.
  • a separate spacer element is used in each case between the directly adjacent rolling elements in a rolling bearing, which is geometrically dimensioned so that it ensures a predetermined minimum distance between the two rolling elements.
  • the spacing elements it is achieved with the spacing elements that a minimum spacing is maintained between two respective adjacent rolling elements and the adjacent rolling elements can not touch each other directly or start up against each other.
  • the individual spacer elements (spacers) can be made extremely thin, which makes it possible to attach a maximum possible number of rolling elements within a rolling bearing and thus to achieve the maximum load capacity for a bearing of given size.
  • each spacer is not rigidly or flexibly connected to the other spacers used in the bearing, so that each spacer element is physically separated from the rest. This also allows easy installation, as well as the spacer elements can be filled or inserted together with the rolling elements in the camp. An additional assembly step for the attachment of the bearing cage can be omitted.
  • spacer elements thus allows the use of the largest possible number of rolling elements without causing an additional high assembly costs.
  • the spacer elements can be inserted or introduced into the bearing next to the rolling elements during the filling or fitting of the rolling bearing. If necessary, in the assembly of the bearing or the outer or inner ring, the spacer element is first introduced in an orientation which is tangent to a bearing pitch circle, between the two bearing rings, in order then to be tilted into a final, radially aligned position. This may be advantageous if a part of the spacer extends in the radial direction into a recess in the bearing inner or in the bearing outer ring. In such embodiments, it is prevented that the spacer can fall out of the warehouse in the assembled state of the bearing.
  • Fig. 1 shows a side view of a ball bearing, ie a view of the bearing in an axial direction.
  • the ball or roller bearing has a bearing inner ring 2 and a bearing outer ring 4.
  • the rolling bearing has a plurality of balls as rolling elements 6.
  • the balls 6 are arranged between the bearing inner ring 2 and the bearing outer ring 4 and rollers on a track which extends in a radial direction 7 by a raceway depth inwards or outwards into the inner or outer ring.
  • the contact surface of the balls 6 with the raceway is indicated here by dashed lines.
  • a spacer 8 is arranged in each case to prevent the adjacent rolling elements 6 touch directly.
  • the minimum distance, which is ensured by the use of the spacer elements 8, is dependent on the geometry of the spacer elements 8 and in particular can be kept extremely small.
  • the minimum distance between adjacent rolling elements 6 occurs here approximately at a bearing pitch circle, which is defined by an idealized circle, which passes through the centers of the individual balls 6 and whose center is located on the axis of rotation of the bearing.
  • each have a separate spacer element 8 is provided, ie, the individual spacer elements 8, which are arranged along the circumference of the rolling bearing, are neither flexible nor rigidly connected and do not touch.
  • the use of individual spacers 8 has the additional advantage that even at high misalignments the performance of the bearing is guaranteed, so that the bearing reliably performs its service even at high misalignments.
  • the contact surfaces of a spacer element 8 so those side surfaces, which face the adjacent rolling elements 6, adapted to the surface contour of the respective adjacent rolling element 6.
  • Adaptation means, for example, that the contours of the mutually contacting or opposite surfaces of the rolling element 6 and the spacer element 8 can be coordinated with one another in such a way that lubrication is improved and the friction between rolling element 6 and spacer element 8 is minimized.
  • the contour of the spacer element 8, for example, the contour of the adjacent rolling element 6 correspond, so as to achieve the largest possible contact surface.
  • the spacer element 8 and the adjacent rolling elements 6 only touch each other at one point.
  • a ratio of the curvatures of the surface of the rolling element 6 and the adjoining surface of the spacer 8 can be set arbitrarily.
  • Fig. 1 By way of example, only four rolling elements 6 with three spacing elements 8 located between them are shown; in alternative embodiments, an arbitrary number of rolling elements 6 and spacing elements 8 can be provided. The remaining rolling elements that fill the bearing were in Fig. 1 not shown for reasons of clarity.
  • the term plurality also describes an exemplary embodiment having a first rolling body, a second rolling body, a third rolling body and a fourth rolling body, wherein a first spacer element between the first rolling element and the second rolling element, a second spacer element between the second rolling element and the third rolling element and a third spacer is disposed between the third rolling element and the fourth rolling element.
  • Fig. 2 shows an embodiment of a selected spacer 9, which in the camp of Fig. 1 is used.
  • FIG. 2 illustrated embodiment is made in two parts and consists of an inner sub-element 10 and an outer sub-element 12.
  • a two-part, selected spacer 9 will be discussed, which, as described above, for example, can be used as the last spacer in the assembly of a rolling bearing, the geometric considerations and considerations apply equally to one-piece spacer elements 8, for example Fig. 1 are shown.
  • Fig. 3 shows a radial section through the selected spacer 9 of Fig. 2 when installed in a ball bearing.
  • the Figures 2 and 3 will be described together below, with reference being made to the respectively more suitable figure for the explanation of the individual features of the spacer 8 and the selected spacer 9.
  • the selected spacer 9 extends opposite to the radial direction 7 in a recess 14 which extends in the radial direction in the bearing inner ring or in the first bearing ring 2.
  • the spacer element in the radial direction 7 additionally or alternatively extends into a recess on the outer ring 4.
  • the recess is presently formed by the running surface for the balls 6.
  • a recess separate from the tread can also be provided in one of the bearing rings, which extends into one of the bearing rings for the purpose of guiding the selected spacer 9.
  • the selected spacing element 9 can be guided during operation of the bearing both on the shoulder, that is to say on an outer annular shoulder 16 or an inner annular shoulder 18, and also on the raceway, that is to say through the recess 14.
  • the selected spacing element 9 or a spacing element 8 can be used in alternative embodiments also by more than one in Fig. 3 illustrated extension length 20 extend into the recess, so that the tread touched by the selected spacer 9 and can be used for leadership.
  • the selected 9 can also be used vice versa, so that it does not extend into the raceway of the bearing inner ring 2 but into the raceway of the bearing outer ring 4.
  • shoulder guide is a radial distance 22 between the selected spacer 9 and the surface of the raceway (a radial air at the lower segment part) greater than 0, to avoid a raceway guidance.
  • the bearing has a defined radial clearance 24 between the outer ring shoulder 16 or inner ring shoulder 18 and the selected spacer element 9. That is, in the radial direction, the dimension of the selected spacer 9 is such that there is a difference between the clearance of the inner race 2 from the outer race 4 and the radial extent of the selected spacer 9, corresponding to the radial clearance 24.
  • the radial clearance 24 can be selected so that a possible jamming or tilting of the selected spacer element 9 in the bearing is prevented by it.
  • falling out of the mounted selected spacer 9 (of the segment) is avoided by having the extension length 20 on the inner sub-member 10 (the lower segment) greater than the radial clearance 24.
  • the illustrated two-part selected spacer 9 has a parting surface 26 on which the inner part element 10 and the outer part element 12 adjoin one another and touch each other.
  • the separating surface 26 is characterized in that it extends predominantly in the axial direction and divides the selected spacer element 9 into two parts, wherein the separating surface 26 in the specific embodiment also does not extend as far as a radial end of one of the partial elements. In other words, in the exemplary embodiment shown, the separating surface 26 extends essentially horizontally (in the axial direction) and not vertically.
  • the separation surface 26 may have a different defined geometric shape, for example, by clamping or crushing individual parts of the inner sub-element 10 or the outer sub-element 12 at Joining the sub-elements to make a permanent connection.
  • the connection of the sub-elements 10 and 12 may be positive, non-positive or cohesive.
  • the separating surface 26 is also formed in the form of a T-groove 28, so that one of the two sub-elements engages in the groove 28 of the other sub-element during assembly.
  • the final connection is made by means of a locking plate 30 which is located at the end of the T-groove 28.
  • the inner part element 10 has a threaded bore 32, by means of which the locking plate 30 can be screwed by a screw 34 against the inner part element 10. As a result, slipping out of the T-slot 28 is prevented and thus the positive connection between the inner sub-element 10 are made to the outer sub-element 12.
  • the adjacent balls 6 facing the contact surface 40 of the selected spacer 9 is further adapted to the spherical surface contour of the adjacent rolling element 6. That is, the contact surface 40 has a similar or identical radius as the adjacent ball 6 in order to ensure good lubrication conditions for the rolling element or for the ball 6.
  • Fig. 4 shows an embodiment of a method according to the invention for mounting a roller bearing using a selected, two-part spacer 9.
  • a first radially inner partial element 10 is arranged between two adjacent rolling elements, so that the first partial element 10 extends counter to a radial direction 7 from a separating surface 26 to a bearing inner ring 2.
  • a second, radially outer sub-element 12 is arranged between the adjacent rolling elements 6, so that the second sub-element 12 extends in the radial direction 7 from the separating surface 26 to the bearing outer ring 4.
  • a connecting step 54c the first sub-element 10 and the second sub-element 12 are connected to one another in a positive, non-positive or cohesive manner.
  • a plurality of rolling elements 6 between a bearing inner ring 2 and a bearing outer ring 4 are arranged.
  • a separate spacer element 8 can be arranged between two respective rolling elements 6 directly adjacent to one another, each spacer element 8 being designed to ensure a predetermined minimum distance between the two adjacent rolling elements 6 and wherein the spacer element 8 is in each case physically separated from all other spacer elements 8 of the rolling bearing is formed.
  • the number of rolling elements in a rolling bearing can be maximized without great expenditure on assembly.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
EP11802879.4A 2010-12-09 2011-12-07 Radialwälzlager mit losen abstandskörpern zwischen den wälzkörpern und verfahren zum zusammenbau des wälzlagers Active EP2649331B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010062712A DE102010062712A1 (de) 2010-12-09 2010-12-09 Wälzlager mit neuem Käfigkonzept und Montageverfahren für ein Lager
PCT/EP2011/072053 WO2012076594A1 (de) 2010-12-09 2011-12-07 Radialwälzlager mit losen abstandskörpern zwischen den wälzkörpern und verfahren zum zusammenbau des wälzlagers

Publications (2)

Publication Number Publication Date
EP2649331A1 EP2649331A1 (de) 2013-10-16
EP2649331B1 true EP2649331B1 (de) 2019-07-17

Family

ID=45440494

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11802879.4A Active EP2649331B1 (de) 2010-12-09 2011-12-07 Radialwälzlager mit losen abstandskörpern zwischen den wälzkörpern und verfahren zum zusammenbau des wälzlagers

Country Status (5)

Country Link
EP (1) EP2649331B1 (https=)
CN (1) CN103339394B (https=)
DE (1) DE102010062712A1 (https=)
IN (1) IN2013CN05400A (https=)
WO (1) WO2012076594A1 (https=)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK2659153T3 (da) 2010-12-27 2017-11-06 Timken Co Lejehus til rulleleje samlet af to trådringe og et antal stiver eller tapper
DK2855954T3 (en) 2012-06-01 2017-08-28 Timken Co IMPROVED DIVIDED RENTAL
DE102013017714A1 (de) * 2013-10-24 2015-04-30 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Wälzlageranordnung mit einem Lagerkäfig sowie Verfahren zur Montage einer solchen Wälzlageranordnung
FR3098263B1 (fr) * 2019-07-03 2021-07-02 Ntn Snr Roulements Procédé de montage ET ensemble mécanique COMPORTANT DES CORPS ROULANTS SÉPARÉS PAR DES ENTRETOISES INDIVIDUELLES
CN116906460A (zh) * 2022-06-10 2023-10-20 山东蓝鲸复合材料科技有限公司 一种十字头轴承

Family Cites Families (13)

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Publication number Priority date Publication date Assignee Title
DD28505A (https=) *
DE185998C (https=) *
DE199184C (https=) * 1900-01-01
DE194484C (https=) * 1900-01-01
DE165758C (de) * 1903-09-26 1905-12-20 Ernst Sachs Kugellagerlaufring
US991061A (en) * 1907-02-28 1911-05-02 Henry Hess Ball-bearing.
US1261154A (en) * 1917-04-19 1918-04-02 John Newmann Ball-bearing.
FR86757E (fr) * 1964-06-26 1966-04-08 S K F Cie D Applic Mecaniques Perfectionnements aux roulements à billes
US4022516A (en) * 1975-09-24 1977-05-10 The Garrett Corporation Bearing spacer and method
SU846836A1 (ru) * 1979-12-26 1981-07-15 За витель Подшипник качени
JP4920250B2 (ja) * 2005-12-16 2012-04-18 Ｎｔｎ株式会社 ころ軸受の組立て方法
CA2581803A1 (en) * 2006-03-13 2007-09-13 Roller Bearing Company Of America, Inc. Tandem stack angular contact bearing for rotary wing aircraft
JP2007271021A (ja) * 2006-03-31 2007-10-18 Nsk Ltd 転がり軸受

Non-Patent Citations (1)

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Title
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Also Published As

Publication number Publication date
CN103339394A (zh) 2013-10-02
DE102010062712A1 (de) 2012-06-14
EP2649331A1 (de) 2013-10-16
IN2013CN05400A (https=) 2015-09-04
CN103339394B (zh) 2016-03-09
WO2012076594A1 (de) 2012-06-14

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